WO2003060266A1

WO2003060266A1 - Hinged door arrester for motor vehicles

Info

Publication number: WO2003060266A1
Application number: PCT/EP2002/014647
Authority: WO
Inventors: Jörg Linnenbrink; Gerhard Rothstein
Original assignee: Friedr. Fingscheidt Gmbh
Priority date: 2002-01-16
Filing date: 2002-12-20
Publication date: 2003-07-24
Also published as: AU2002367037A1; DE10296304D2

Abstract

The invention relates to a hinged door arrester, especially for vehicle doors. Said hinged door arrester is comprised of two hinge parts (2, 4) which are connected by a hinge pin (6) in a manner that permits them to pivot about a rotational axis (8) and a retainer (10) for mutually arresting the hinge parts (2, 4) in different relative rotational positions. The retainer (10) is mounted laterally off-set with respect to the hinge pin (6) and comprises, on a bearing axis (18) parallel to the hinge pin (6), two retainer elements (12, 14) that engage with each other. A relative pivoting movement of the hinge parts (2, 4) rotatably drives, via a drive (20), at least one (14) of the retainer elements (12, 14) relative to the other retainer element (12) about a rotational axis (22) that is determined by the bearing axis (18) and parallel to the rotational axis (8). The bearing axis (18) is linked with the first hinge part (2) in such a manner that it is displaced on an orbit about the hinge rotational axis (8) relative to the second hinge part (4). The drive (20) for the retainer (10) is a toothed gear (30) that is mounted on the bearing axis (18) and that interacts with an internal gearing (32) linked with the second hinge part (4).

Description

'Hinge door holder for motor vehicles'

The present invention relates to a hinge door holder, in particular for vehicle doors, consisting of two hinge parts pivotally connected by means of a hinge pin about an axis of rotation and a holding device for mutually locking the hinge parts in different relative rotational positions, the holding device being arranged laterally offset with respect to the hinge pin and on one of them Hinge pin parallel bearing axis has two interacting holding elements, in particular engaging in the axial direction, with relative pivoting movements of the hinge parts via drive means driving at least one of the holding elements relative to the other holding element about a rotation axis determined by the bearing axis and parallel to the axis of rotation.

Such a hinge door holder or a "door lock for motor vehicle doors connected to a door hinge" is known for example from DE 198 54 602 A1. In this case, locking elements of the holding or locking device interact via rolling elements, specifically via tapered rollers rotatably mounted about radial axes. One locking element is rotatably guided on the bearing axis and is driven directly by the hinge pin in that a toothed ring seated on the hinge pin is in engagement with an external toothing of the locking element. It is a decisive disadvantage of this embodiment that very high or moments act in the area of the gears.

DE 100 09 375 A1 also describes a similar door holder, in which even both locking elements are driven in opposite directions via a gear of the hinge pin. In one case, this is done via an idler gear, which reverses the direction of rotation.

The present invention has for its object to provide a hinge door holder of the type mentioned, which under manageable forces or Torque ratios optimized usage properties and in particular ensures a stepless or at least "quasi-stepless" locking.

According to the invention, this is achieved in that the bearing axis is connected to the first hinge part in such a way that it can be moved in a circular path about the hinge axis of rotation relative to the second hinge part, with a gearwheel seated on the bearing axis with a drive mechanism for the holding device the second hinge part connected internal teeth cooperates.

This advantageous embodiment enables an extremely favorable transmission ratio to be achieved in the area of the drive means in that a large number of teeth in relation to the gearwheel is effectively possible due to the internal toothing. The gear ratio can be particularly advantageously in the range from 2/1 to 4/1. Advantageously, the force acting on the drive means is also reduced in the same ratio. In addition, a translation is achieved in such a way that correspondingly more stop marks or relative rotational positions can be effectively implemented across the swivel angle range of the hinge parts. As a result, there is almost no steplessness.

Further advantageous design features and advantages are contained in the subclaims and the following description.

The invention will be explained in more detail by way of example with reference to the drawing. Show:

1 is a partial axial section of a hinge door holder according to the invention,

2 shows a cross section in the plane II-II according to FIG. 1,

Fig. 3 shows a detail of the area III in Fig. 1 in an advantageous

Further education,

4 shows a separate illustration of an individual part according to FIG. 3 in an advantageous development, 5 is a plan view in the direction of arrow V according to FIG. 4,

6 is an enlarged section in the plane VI - VI of FIG. 5,

7 is an exploded perspective view of the individual parts shown in FIG. 6,

8 a partially cut open (in the area of the holding device)

Perspective view of a further embodiment of the hinge door holder according to the invention,

9 is a separate representation of an individual part of the holding device in an advantageous embodiment,

10 is an enlarged detail of FIG. 9,

11 a-c sectional views of the holding device according to FIG. 9 in different engagement states,

Fig. 12 u. 13 representations analogous to FIG. 9 in alternative versions,

1 ^' 4 shows a section in the plane XIV - XIV according to FIG. 13 and

15 a-c sectional views XV - XV according to FIG. 12 in different engagement states (similar to FIG. 11).

1, a hinge door holder according to the invention consists of a first hinge part 2 and a second hinge part 4, these two hinge parts 2, 4 being pivotally connected about an axis of rotation 8 by means of a hinge pin 6. In the example shown, the hinge pin 6 is with. the first hinge part 2 rotatably connected, while the second hinge part 4 is rotatably guided on the hinge pin 6. The hinge parts 2, 4 can be connected on the one hand to a vehicle frame and on the other hand to a vehicle door, the assignment being basically arbitrary.

The hinge door holder further has a holding device 10 for mutually locking the hinge parts 2, 4 in different relative rotational positions. The In this embodiment, holding device 10 consists of two holding elements 12 and 14 interacting in the axial direction. In the example shown, holding elements 12, 14 interact axially directly with sliding friction, wherein they are preferably designed in the manner of a non-positive slip clutch. This means that the two in particular rotationally symmetrical holding elements 12, 14 z. B. axially interact with sliding friction via spur toothing 16 or the like. These spur gears 16 have the largest possible division of the circumference in order to ensure as many engagement positions as possible over the swivel angle range in view of the desired “quasi-steplessness”.

The holding device 10 is arranged laterally offset with respect to the hinge pin 6. The holding elements 12, 14 sit on a bearing axis 18 parallel to the hinge pin 6, so that by means of relative pivoting movements of the hinge parts 2, 4 via drive means 20, at least one of the holding elements 12, 14 relative to the other by one defined by the bearing axis 18 to the Hinge axis of rotation 8 parallel axis of rotation 22 is driven in rotation.

Due to the illustrated and preferred embodiment, by pivoting the second hinge part 4 relative to the first hinge part 2, the second holding element 14 is rotated relative to the first holding element 12 (cf. double arrow 24). Via the spur gears 16, this leads to the second holding element 14 being moved in an oscillating manner in the axial direction of engagement (double arrow 26). This movement can (but does not have to) take place against the force F of an energy store 28. The force F is intended to keep the spur gears 6 engaged.

The bearing axis 18 is connected to the first hinge part 2 in such a way that it can be moved on a circular path about the hinge axis of rotation 8 - compare in particular FIG. 2 and the double arrow 29 shown there - relative to the second hinge part 4. During these movements, a gearwheel 30 seated on the bearing axis 18 interacts with the drive means 20 for the holding device 10 with an internal toothing 32 which is connected to the second hinge part 4 and is curved coaxially in a circular arc shape to the hinge axis of rotation 8. In the preferred embodiment according to FIG. 1, the second hinge part 4 is designed like a housing, the holding device 10 being movably accommodated within this housing. The internal toothing 32 is in the area of a hinge pin 6 opposite wall 34 arranged. 2, the housing-like hinge part 4 has an approximately quarter-circular or circular sector-shaped cross section. The bearing axis 18 is guided via a guide part 36 which is connected in a rotationally fixed manner to the first hinge part 2 or to the hinge pin 6 and is therefore pivotable about the axis of rotation 8 relative to the second hinge part 4. 1, this guide part 36 has an approximately cylindrical or tubular holding section 38, which is seated on the hinge pin 6, and two guide webs 40, which extend radially therefrom and are spaced apart from one another in parallel. The bearing shaft 18 is seated at the end in coaxial bearing openings of the guide ribs 40. Preferably sits the gear 30 rotatably mounted on the bearing shaft 18, the bearing axis 18 to ^"22 is mounted rotatably in the bearing holes of the guide webs 40 its axis of rotation. Furthermore, it is provided that one , due to the relative hinge-pivoting movements, the holding element 14, which is axially moved against the energy accumulator 28, is seated in a rotationally fixed but longitudinally movable manner on the bearing axis 18, while the other holding element 12 is connected to the guide part 36 in a manner fixed against relative rotation and in particular in the axial direction An axial connecting pin 42 is arranged between the guide web 40 and the holding element 12 seated thereon as an anti-rotation device.

This preferred embodiment advantageously ensures that the gearwheel 30 can be designed with a number of teeth which is relatively small relative to the number of teeth of the internal toothing 32, which is based on the entire 360 ° circumference. This allows a very favorable gear ratio (> 1: 1) of the drive means 20 z. B. in the range of 2: 1 to 4: 1 can be achieved. Accordingly, only VA to Vz of the force F occurs in the holding elements in the toothing region. In addition, based on the transmission ratio based on the maximum swivel angle range of the hinge parts 2, 4 of, for example, approximately 70 degrees, correspondingly more locking positions can be guaranteed, that is to say at least 8 to 16 engagement positions. The hinge door holder according to the invention thus works “quasi-continuously”.

In connection with the embodiment described so far, it is also advantageous if an additional damping device 50 is provided for damping the movement of the holding element 14 which is axially movable in the direction of engagement. This damping device 50 is arranged axially between the axially movable holding element 14 and the preferably available energy store 28 in such a way that by an initial relative pivoting movement, the movable holding element 14 is moved axially via the damping device 50 against the energy accumulator 28, but then the damping device 50 dampens or delays the force F of the energy accumulator 28 to the holding element 14 in such a way that this movable holding element 14 during a dynamic pivoting movement is essentially free of the force F of the energy accumulator 28 and is only damped again or the force F is applied again after the pivoting movement has ended. As a result, dynamic swiveling movements are almost free-moving, ie practically without intervention of the holding elements.

In the preferred embodiment shown, the damping device 50 is formed by a spindle gear 52. For this purpose, reference is also made to FIGS. 3 to 7. The spindle gear 52 consists of a central spindle 54 connected to the bearing axis 18 or formed by a portion of the bearing axis 18 and a spindle nut 56 seated on the spindle 54. The axially movable holding element 14 acts - preferably via an axial rotary bearing 58 - against the spindle nut 56, which in turn acts - preferably via a further axial rotary bearing 60 - against the energy accumulator 28. The axial rotary bearings 58, 60 can - as shown (see Fig. 3) - be designed as roller bearings (ball bearings) or - for a possibly desired additional friction - as a plain bearing (friction discs). In this case, the spindle gear 52 has a thread pitch such that the axial force which occurs when the holding element 14 is moved axially is free-wheeling, i. H. causes the spindle nut 56 to rotate automatically. The rotation then causes the spindle nut 56 to move against the energy accumulator 28 in accordance with the thread pitch. According to the thread pitch, damping of the return movement or the spring force F is advantageously achieved. It is particularly advantageous here if the thread pitch is only slightly outside the range of the self-locking, that is to say is as flat as possible, because optimal, very effective damping is thereby achieved.

In a further advantageous embodiment (FIG. 3), the spindle gear 52 can also have additional damping 62, for example in the form of a brake acting on the spindle nut 56. The example shown is a mechanical friction brake which acts radially against the spindle nut 56. As illustrated in FIGS. 4 to 7, the spindle gear 52 is configured in a preferred embodiment with regard to an axial play in a self-adjusting manner. This always ensures a direct flow of force between the holding element 14 and the spring accumulator 28 via the damping device 50. As can be seen in particular from FIGS. 6 and 7, the spindle nut 56 is formed in several parts with spindle nut halves 64, 66 which can be braced against one another and are under torsional prestress V. The spindle nut half 64 forms a lower part with an outer ring web 70 having an internal thread 68, into which a clamping element 72 with an external thread 74 can be screwed. The clamping element 72 acts against the other spindle nut half 66. The spindle 54 preferably has only individual thread sections 76 instead of a continuous thread, to which corresponding counter-thread sections 78 of the spindle nut halves 64, 66 are assigned. Suitable means (not shown), such as a torsion spring or the like, are provided for generating the torsional pretension in the closing direction or clearance direction.

The thread or thread sections 76 and mating thread sections 78 are preferred and, as shown, are designed in the manner of a trapezoidal thread.

As an alternative to the preferred embodiments shown, a holding device can also be used, the holding elements of which interact with rolling friction with rolling elements. In principle, radially acting holding elements can also be provided.

In an advantageous further development of the invention, which is only indicated in FIGS. 4 and 5, as an alternative or in addition to the energy store 28, a special device 80 is provided for generating a holding force acting on the holding element 14 in the locking direction. This holding force acts mainly in the engagement position of the holding elements 12, 14 and can thus replace or support the force F of the energy store 28, which is advantageous in that the force F of the energy store 28 in the engagement position is disadvantageously less than in the lifting position of the holding element 14 is. This is advantageously compensated for by the holding force and a high holding torque is ensured. In this case, however, this device 80 is advantageously designed such that the holding force arises only or mainly in the area of the engagement position, while in the axially raised position the holding element 14 is essentially free of the holding force. As a device 80 for Generation of the holding force can be provided, for example, a magnet arrangement, the spindle nut 56 carrying a first active element 82 on its outer circumference and a second, magnetically correspondingly corresponding active element 84 being held on the housing side in such a way that, in the engagement position, both active elements 82, 84 lie against one another in a magnetically attractive manner. This design has the advantage that the holding force occurs only or mainly in the engaged position. In addition, shortly before reaching the engagement position, the spindle nut 56 is actively driven in the direction of rotation by a torque M such that reaching the engagement position is accelerated or supported. A maximum holding force therefore really only works when it is needed, while an at least significantly reduced force acts in the respective raised intermediate latching positions. This results in minimal wear of the holding elements.

In the embodiment of the hinge door holder shown in FIG. 8, the holding device 10, in the manner of a multi-disc clutch, consists of at least three, for example five, holding elements 12, 14 as shown. These holding elements 12, 14 lie one above the other in a packet-like sequence, with two directly adjacent holding elements in each case are movable relative to each other and cooperate locking. As a result, a plurality of engagement planes 90 are advantageously formed. The holding members 12, 14 in _two groups are more specifically divided, wherein the first group of holding elements 12 with the first hinge part 2 and the second group are connected by support members 14 with the second hinge part 4, wherein the holding elements of the two groups alternately arranged are. This preferred embodiment ensures that the holding force generated by the energy store 28 and / or the device 80 is practically multiplied by the number of engagement levels 90, so that overall a high holding torque is ensured in the blocked position even with a low holding force. In this case, it can also be advantageous if the holding elements of at least one of the two groups (12 and / or 14) are arranged rotated relative to one another, in such a way that this eliminates play (toothing play) of the holding device 10. As a result, the door is defined in the blocked position, held very precisely without play.

As can further be seen from FIG. 8, in this embodiment the holding elements 14 interact directly with the internal toothing 32, for which purpose they have an external toothing - replacing the gearwheel 30 described above. As can be seen from the detailed illustrations in FIGS. 9 to 15, the holding elements 12, 14 can advantageously be designed in the area of their interacting engagement surfaces in such a way that a minimum surface pressure (force per surface) is achieved by the holding elements 12, 14 always lie as close together as possible. In the embodiment according to FIGS. 9 to 11, this is achieved in that the holding elements 12, 14 have cooperating spur gears, the tooth sections 92 of which are designed as thread cutouts, in particular in the manner of a trapezoidal thread (half trapezoidal geometry). The tooth sections 92 according to FIG. 10 can each have two tooth flanks 92a and 92b, which are designed to be of different steepnesses such that holding torques of different sizes are achieved in the closing and opening direction of the door. In this embodiment, according to FIG. 11, the tooth sections 92 are always in planar, but at least linear, contact.

In the embodiment variant according to FIGS. 12 to 15, the holding elements 12, 14 have cooperating negative contours on the one hand with depressions 94 and on the other hand with projections 96 that fit into the depressions 94 (standard geometry). According to FIG. 15a, a large-area contact is also achieved hereby - at least in the engagement position.

In both variants according to FIGS. 9 and 12 to 15, only the device 80, ie not the force accumulator 28, is preferably provided to generate the holding force. It is advantageous here that the holding force actually only acts in the engaged position, that is to say when the holding elements 12, 14 lie against one another with a maximum large contact surface. This leads to the desired minimal surface pressure. If the holding elements 12, 14 are then in motion due to movement with a smaller area or only at least linearly in contact, the holding force is practically zero, so that the surface pressure is then also small. This significantly reduces wear due to friction.

For the rest, the invention is not limited to the illustrated and described design features, but also encompasses all designs having the same effect in the sense of the invention. Furthermore, the invention has not yet been limited to the combination of features defined in claim 1, but can also be combined by any other combination of specific features disclosed individual features can be defined. This means that in principle practically every individual feature of claim 1 can be omitted or replaced by at least one individual feature disclosed elsewhere in the application. The claims are therefore only to be understood as a first attempt at formulation.

Claims

Expectations

1. Hinge door holder, in particular for vehicle doors, consisting of two hinge parts (2, .4) pivotably connected by means of a hinge pin (6) about an axis of rotation (8) and a holding device (10) for mutually locking the hinge parts (2, 4) in different Relative rotational positions, the holding device (10) being laterally offset with respect to the hinge pin (6) and having two engaging interacting holding elements (12, 14) on a bearing axis (18) parallel to the hinge pin (6), the hinge parts (16) being pivoted relative to one another. 2, 4) via drive means (20) at least one (14) of the holding elements (12, 14) relative to the other holding element (12) about a rotation axis (22) determined by the bearing axis (18) and parallel to the axis of rotation (8) is driven in rotation, characterized in that the bearing axis (18) is connected to the first hinge part (2) so that it is in a circular path around the hinge rotation sleeve (8) can be moved relative to the second hinge part (4), a gear (30) seated on the bearing axis (18) with an internal toothing connected to the second hinge part (4) serving as drive means (20) for the holding device (10) (32) interacts.

2. Hinge door holder according to claim 1, characterized in that the bearing axis (18) is guided via a rotationally fixed to the first hinge part (2) and thereby relative to the second hinge part (4) about the axis of rotation (8) pivotable guide part (36) ,

3. Hinge part according to claim 1 or 2, characterized in that the gear (30) is non-rotatably on the bearing axis (18) and the bearing axis (18) is rotatably mounted about its axis of rotation (22).

4. Hinge door holder according to one of claims 1 to 3, characterized in that the holding elements (12, 14) cooperate in the axial direction and in particular by an energy store (28) are axially loaded, the one holding element (14), which is moved axially, in particular against the energy accumulator (28), by the pivoting movements preferably being seated in a rotationally fixed and longitudinally movable manner on the bearing axis (18), while the other holding element (12) is non-rotatably and in particular axially is fixedly connected to the guide part (36).

Hinge door holder according to one of claims 1 to 4, characterized in that the drive means between the internal toothing (32) and the gear (30) have a transmission ratio of greater than 1: 1, in particular approximately in the range from 2: 1 to 4: 1.

Hinge door holder according to one of claims 1 to 5, g e ke n n ze i ch n et d u rch by a damping device (50) for damping the engagement movements of the movable holding member (14).

Hinge door holder according to claim 6, characterized in that the damping device (50) acts on the movable holding element (14) in such a way that the movable holding element (14) moves away from the other holding element (12) by an beginning relative pivoting movement and in this position during a dynamic pivoting movement essentially remains and only moves back against the other holding element (12) after the pivoting movement has ended.

Hinge door holder according to claim 6 or 7, characterized in that the damping device (50) is arranged between the movable holding element (14) and a force accumulator (28) such that the movable holding element (14) via the damping device (50 ) is moved against the energy accumulator (28) and then the damping device (50) transmits the force (F) of the energy accumulator (28) damped to the holding element (14) in such a way that the movable holding element (14) is essentially free during a dynamic pivoting movement of the force (F) of the energy accumulator (28) and is damped or delayed with the force (F) only after the swiveling movement has ended. Hinge door holder according to one of claims 6 to 8, characterized in that the damping device (50) is formed by a spindle gear (52).

Hinge door holder according to claim 9, characterized in that the spindle gear (52) consists of a central spindle (54) connected to the bearing axis (18) and a spindle nut (56) seated on the spindle (54), the movable holding element ( 14) - in particular via an axial rotary bearing (58) - act against the spindle nut (56) and on the other hand the spindle nut (56) - in particular via an axial rotary bearing (60) - against the energy accumulator (28).

Hinge door holder according to claim 9 or 10, so that the spindle gear (52) is designed to be self-adjusting with respect to an axial play.

Hinge door holder according to claim 11, so that the spindle nut (56) is constructed in several parts with spindle nut halves (64, 66) which can be braced against one another and in particular are under a corresponding torsional preload (V).

Hinge door holder according to one of claims 9 to 12, characterized in that the spindle gear (52) has a thread pitch which ensures free running under axial force, but is preferably only slightly outside the self-locking.

Hinge door holder according to one of claims 9 to 13, characterized in that the spindle gear (52) has an additional damping (62) in particular in the form of a brake acting on the spindle nut (56).

Hinge door holder according to one of claims 1 to 14, characterized in that the holding elements (12, 14) interact directly with sliding friction. Hinge door holder according to one of claims 1 to 15, characterized in that the holding device (10) is designed in the manner of a force-fitting slip clutch, the two in particular rotationally symmetrical holding elements (12, 14) interacting axially with sliding friction via spur toothing (16) or similar detents.

Hinge door holder according to one of claims 1 to 14, characterized in that the holding elements (12, 14) interact with rolling friction with rolling elements.

Hinge door holder according to one of claims 1 to 17, characterized by a device (80) designed to generate a holding force acting on the holding element (14) in the engagement direction in such a way that the holding force is generated only or mainly in the latching engagement position of the holding elements (12, 14).

Hinge door holder according to claim 18, d a d u rch g e ke n n ze i ch n et, that the holding force on the spindle gear (52) is generated by a magnetic torque (M) in particular the spindle nut (56).

Hinge door holder according to one of claims 1 to 19, characterized in that the holding device (10) in the manner of a multi-disc clutch consists of at least three stacked holding elements (12, 14) one above the other, each with two directly adjacent holding elements (12, 14) being movable relative to one another and interact in an intervening manner so that a plurality of engagement planes (90) are formed.

Hinge door holder according to one of claims 1 to 20, characterized in that the holding elements (12, 14) are divided into two groups, the first group of holding elements (12) with the first hinge part (2) and the second group of holding elements (14 ) are connected to the second hinge part (4), and wherein the holding elements (12, 14) of the two groups are arranged in an alternating order.

Hinge door holder according to one of claims 1 to 21, characterized in that the holding elements (12, 14) of at least one of the two groups are arranged so as to be slightly rotated relative to one another in order to eliminate a play in movement of the holding device (10).

Hinge door holder according to one of claims 1 to 22, dad u rch. marked that the holding elements (12, 14) are designed such that a minimal surface pressure is achieved.

Hinge door holder according to claim 23, characterized by the fact that the holding elements (12, 14) have cooperating end serrations, the tooth sections (92) of which are designed as thread cutouts, in particular in the manner of a trapezoidal thread, so that a maximum area contact is ensured in the engagement position, which continuously merges into an at least linear system in the case of relative movement.

Hinge door holder according to claim 24, characterized in that the toothed sections (92) each have two tooth flanks (92a, 92b) which are designed to be of different steepness such that holding moments of different sizes are achieved in the closing and opening directions of the door.

Hinge door holder according to claim 23, characterized in that the holding elements (12, 14) • negative contours interacting in this way have, on the one hand, with depressions (94) and, on the other hand, with projections (96) that fit into the depressions (94) in such a way that in each relative position there is an at least linear shape System and at least in the engagement position a maximum large area system is guaranteed.